U.S. patent application number 17/006939 was filed with the patent office on 2021-05-13 for winch.
The applicant listed for this patent is Zhejiang Runva Mechanical & Electrical Co., Ltd. Invention is credited to Linji Dai, Ling Ye, Zhilin Yu, Xiaobin Zhang.
Application Number | 20210139298 17/006939 |
Document ID | / |
Family ID | 1000005066155 |
Filed Date | 2021-05-13 |
![](/patent/app/20210139298/US20210139298A1-20210513\US20210139298A1-2021051)
United States Patent
Application |
20210139298 |
Kind Code |
A1 |
Yu; Zhilin ; et al. |
May 13, 2021 |
Winch
Abstract
A winch includes a coupling A, a coupling B, a rectangular
spring, a gear wheel, a gear rack, a friction ring, and a
transmission shaft, etc. By increasing the distance between the
adjacent internal teeth of the two-stage planet carrier, it ensures
that the three-stage sun gear can be smoothly inserted into the
two-stage planet carrier even if the elasticity of spring A is
reduced, such that the engagement width between the three-stage sun
gear and the two-stage planet carrier can reach the normal
requirements. With the design of sliding gear ring and spring C, it
can greatly reduce the phenomenon of mis-engagement when the
external teeth of the three-stage sun gear enter the internal teeth
spacing of the two-stage planet carrier, protect the teeth
integrity of the three-stage sun gear and the two-stage planet
carrier.
Inventors: |
Yu; Zhilin; (Jinhua, CN)
; Dai; Linji; (Jinhua, CN) ; Zhang; Xiaobin;
(Jinhua, CN) ; Ye; Ling; (Jinhua, CN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Zhejiang Runva Mechanical & Electrical Co., Ltd |
Jinhua |
|
CN |
|
|
Family ID: |
1000005066155 |
Appl. No.: |
17/006939 |
Filed: |
August 31, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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PCT/CN2019/119782 |
Nov 20, 2019 |
|
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17006939 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B66D 1/485 20130101;
B66D 1/225 20130101 |
International
Class: |
B66D 1/22 20060101
B66D001/22; B66D 1/48 20060101 B66D001/48 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 7, 2019 |
CN |
201911079095.X |
Claims
1. A winch, comprising: a housing, an electric control module
mounted in the upper side of the housing, a motor module mounted in
the left end side of the housing and a deceleration module and a
clutch mounted in the right end side of the housing, and a drum
mounted in the middle of the lower side of the housing, wherein the
motor in the motor module drives the transmission shaft in the drum
to rotate through a brake unit, the transmission shaft drives the
drum to rotate through the deceleration module, and the clutch
controls the axial movement of the transmission shaft; wherein the
deceleration module is composed of a one-stage deceleration
assembly, a two-stage deceleration assembly and a three-stage
deceleration assembly; a sliding gear ring is slidably mounted in a
two-stage planet carrier in the two-stage deceleration assembly,
and the external teeth of the sliding gear ring are always in
engagement with internal teeth in the two-stage planet carrier; one
end of a spring C located in the two-stage planet carrier is
connected to the sliding gear ring, and the other end is connected
to the inner ring of the center hole of the two-stage planet
carrier; a three-stage sun gear in the three-stage deceleration
assembly mates with a convex wear ring on the side of the sliding
gear ring; the three-stage sun gear always follows the transmission
shaft for synchronous axial movement; the size of any one of
external teeth on the three-stage sun gear is smaller than the
spacing between any two adjacent internal teeth of the two-stage
planet carrier; the brake unit comprises a coupling A, a coupling
B, a rectangular spring, a gear wheel, and a gear rack, wherein a
convex column A is disposed on the side of disk A of the coupling
A, and two arc blocks A are symmetrically disposed on the outer
cylindrical surface of the convex column A; a convex column B is
disposed on one side of disk B of the coupling B, and two arc
blocks B are symmetrically disposed on the other side; one end of
the transmission shaft is slidably mounted in the chute B of the
convex column B; spring A is mounted between the groove surface of
the chute B and the corresponding end surface of the transmission
shaft is always in a compressed state; a circular cavity is
disposed in the disk B, and two chutes A are symmetrically provided
in the center on the inner ring surface of the circular cavity; two
arc blocks B are sleeved on the convex column A, and the two arc
blocks B mate with two arc blocks A respectively; one end of a
rotary shaft is fixedly connected to the end of the convex column A
away from the disk A, and the other end penetrates into the
circular cavity of the disk B and is fixedly equipped with a gear
wheel; two gear racks engaged with the gear wheel slide on the two
chutes A, respectively; the ends of two gear racks away from each
other are slidably mounted with a sliding block through a spring B;
one end of a rectangular spring sleeved on the arc block A and the
arc block B is connected with an arc block A, and the other end is
connected with an arc block B; a bracket is disposed in the housing
and a friction ring is disposed at the center of the side of the
bracket, the friction ring is located in the drum; the coupling A
and the coupling B are both located in the friction ring; two tooth
sockets are provided symmetrically in the center of the inner ring
surface at one end of the friction ring; two sliding blocks on the
two gear racks mate with the two tooth sockets respectively; the
rectangular spring mates with the friction ring.
2. The winch according to claim 1, wherein the transmission shaft
is provided with a ring groove A and a ring groove B; a snap ring A
and a snap ring B are mounted in the ring groove A and ring groove
B of the transmission shaft respectively; a convex ring is disposed
on the side of the snap ring A and the convex ring is sleeved on
the transmission shaft; the outer ring surface of the convex ring
is mounted with a thrust bearing; the three-stage sun gear is
sleeved on the transmission shaft and the three-stage sun gear is
located between the thrust bearing and the snap ring B; one side of
the three-stage sun gear is in contact with the thrust bearing, and
the other side is in contact with the snap ring B.
3. The winch according to claim 1, wherein one of the two arc
blocks A has a notch A; and one of the two arc blocks B has a notch
B; the notch A is located oppositely to the notch B; one end of the
rectangular spring is fixedly mounted in the notch A of the arc
block A, and the other end is fixedly mounted in the notch B of the
arc block B.
4. The winch according to claim 1, wherein two guide grooves are
provided symmetrically inside the chute B of the convex column B;
two guide blocks are disposed symmetrically on the outer wall at
one end of the transmission shaft in the chute B; the two guide
blocks slide in the two guide grooves respectively.
5. The winch according to claim 1, wherein the chute B of the
convex column B is internal regular hexagonal, the outer wall of
the transmission shaft is external regular hexagonal, and the outer
wall of the transmission shaft and the inner wall of the chute B
are surface-to-surface sliding.
6. The winch according to claim 1, wherein two guide rails are
mounted symmetrically in the center of inner ring surface of the
circular cavity in the disk B; the two guide rails are in
communication with the two chutes A respectively; the two gear
racks slide on the two guide rails respectively.
7. The winch according to claim 1, wherein a telescopic groove is
provided at one end of the gear rack; the sliding block is slidably
mounted in the telescopic groove; one end of the spring B located
in the telescopic groove is connected to the telescopic groove
surface, and the other end is connected to the sliding block.
8. The winch according to claim 1, where the outer wall of the
rectangular spring is a friction surface; one end of the tooth
socket is a straight groove face, and the other end is an arc
groove face; the end of the sliding block away from the spring B is
a cambered surface.
9. The winch according to claim 1, wherein the clutch is composed
of a clutch handle, a clutch sleeve and a clutch slider; the outer
side of the housing is rotatably mounted with a clutch handle, and
the clutch sleeve located in the housing is fixedly connected with
the clutch handle; two spiral structures are symmetrically disposed
on the clutch sleeve; the clutch slider is slidably mounted in the
housing along the axial direction of the transmission shaft, the
two spiral structures on the clutch sleeve mate with the clutch
slider such that the clutch slider moves axially; the axial
movement of clutch slider is controlled by rotating the clutch
handle to drive the clutch sleeve to rotate.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] The present application is a Continuation Application of PCT
Application No. PCT/CN2019/119782 filed on Nov. 20, 2019, which
claims the benefit of Chinese Patent Application No. 201911079095.X
filed on Nov. 7, 2019, the contents of which are incorporated
herein by reference in their entirety.
FIELD OF THE INVENTION
[0002] The present invention relates to the general technical field
of winch, and specifically relates to a winch.
BACKGROUND
[0003] At present, in the current winches, the principle of the
power connection or clutch between the deceleration component and
the intermediate transmission shaft in the winch is to realize the
clutch by changing the engagement relationship between a
three-stage sun gear and a two-stage planet carrier. When the
three-stage sun gear and the two-stage planet carrier are switched
from a separation state to a reunion state, the three-stage sun
gear cannot enter the two-stage planet carrier to produce
engagement; in this case, the twisted rope needs to be manually
pulled to rotate the drum, so that the drum can drive the
three-stage sun gear to rotate a certain angle by the three-stage
planet carrier and the three-stage planetary gear, and the
three-stage sun gear can enter the two-stage planet carrier to
produce engagement. However, when the above operation is improper
or the rope pulling is forgotten and the motor is energized, the
three-stage sun gear quickly enters the two-stage planet carrier to
produce engagement, and the speed of the three-stage sun gear is
related to the spring elasticity at the coupling. When the spring
at the coupling becomes weak due to long-term use, the speed of the
three-stage sun gear entering the two-stage planet carrier will
slow down. At this time, when the internal teeth of the two-stage
planet carrier are in contact with the three-stage sun gear
external teeth and start transmission, it is very likely that the
three-stage sun gear has not been inserted appropriately. The
friction is generated due to the pressure of teeth engagement
between the three-stage sun gear and the two-stage planet carrier
during the transmission process. The inadequate force of the
three-stage sun gear inserted into the two-stage planet carrier
will inevitably lead to insufficient width of engagement generated
between the three-stage sun gear and the two-stage planet carrier.
If such state lasts for a long time, the teeth of the three-stage
sun gear and the two-stage planet carrier will be inevitably
damaged, and the winch cannot be used normally.
[0004] In addition, the brake unit in the winch is to brake the
intermediate transmission shaft and friction ring. During the
braking, the drum is pulled by the twisted rope, the rotating drum
drives the intermediate transmission shaft to rotate through the
deceleration component, and the intermediate transmission shaft
brakes through the brake unit and friction ring. During the
braking, due to the friction between the rectangular spring and the
friction ring in the brake unit, the rectangular spring is prone to
heat by friction and fails.
[0005] The present invention designs a winch to solve the above
problems.
SUMMARY
[0006] In order to solve the shortcomings of the prior art, the
present invention discloses a winch, which is achieved by the
following technical solutions.
[0007] In the present invention, it should be noted that, the terms
"interior", "lower", "upper" and others indicating the orientation
or positional relationship are based on the orientation or
positional relationship shown in the drawings, or the customary
orientation or positional relationship of the product herein, which
is only for describing the present invention and simplifying the
description, but not indicate or imply that the device or element
referred to must have a specific orientation, or must be configured
or operated in a specific orientation, therefore, it cannot be
understood as limiting the present invention. In addition, the
terms "first", "second", etc. are only used for distinguishing, but
cannot be understood as indicating or implying relative
importance.
[0008] A winch, comprising: a housing, an electric control module
mounted in the upper side of the housing, a motor module mounted in
the left end side of the housing and a deceleration module and a
clutch mounted in the right end side of the housing, and a drum
mounted in the middle of the lower side of the housing, the motor
in the motor module drives the transmission shaft in the drum to
rotate through a brake unit, the transmission shaft drives the drum
to rotate through the deceleration module, and the clutch controls
the axial movement of the transmission shaft; wherein the
deceleration module is composed of a one-stage deceleration
assembly, a two-stage deceleration assembly and a three-stage
deceleration assembly; a sliding gear ring is slidably mounted in a
two-stage planet carrier in the two-stage deceleration assembly,
and the external teeth of the sliding gear ring are always in
engagement with internal teeth in the two-stage planet carrier; one
end of a spring C located in the two-stage planet carrier is
connected to the sliding gear ring, and the other end is connected
to the inner ring of the center hole of the two-stage planet
carrier; a three-stage sun gear in the three-stage deceleration
assembly mates with a convex wear ring on the side of the sliding
gear ring; the three-stage sun gear always follows the transmission
shaft for synchronous axial movement; the size of any one of
external teeth on the three-stage sun gear is smaller than the
spacing between any two adjacent internal teeth of the two-stage
planet carrier.
[0009] The brake unit comprises a coupling A, a coupling B, a
rectangular spring, a gear wheel, and a gear rack, wherein a convex
column A is disposed on the side of disk A of the coupling A, and
two arc blocks A are symmetrically disposed on the outer
cylindrical surface of the convex column A; a convex column B is
disposed on one side of disk B of the coupling B, and two arc
blocks B are symmetrically disposed on the other side; one end of
the transmission shaft is slidably mounted in the chute B of the
convex column B; spring A is mounted between the groove surface of
the chute B and the corresponding end surface of the transmission
shaft is always in a compressed state; a circular cavity is
disposed in the disk B, and two chutes A are symmetrically provided
in the center on the inner ring surface of the circular cavity; two
arc blocks B are sleeved on the convex column A, and the two arc
blocks B mate with two arc blocks A respectively; one end of a
rotary shaft is fixedly connected to the end of the convex column A
away from the disk A, and the other end penetrates into the
circular cavity of the disk B and is fixedly equipped with a gear
wheel; two gear racks engaged with the gear wheel slide on the two
chutes A, respectively; the ends of two gear racks away from each
other are slidably mounted with a sliding block through a spring B;
one end of a rectangular spring sleeved on the arc block A and the
arc block B is connected with an arc block A, and the other end is
connected with an arc block B;
[0010] A bracket is disposed in the housing and a friction ring is
disposed at the center of the side of the bracket, the friction
ring is located in the drum; the coupling A and the coupling B are
both located in the friction ring; two tooth sockets are provided
symmetrically in the center of the inner ring surface at one end of
the friction ring; two sliding blocks on the two gear racks mate
with the two tooth sockets respectively; the rectangular spring
mates with the friction ring.
[0011] Preferably, the transmission shaft is provided with a ring
groove A and a ring groove B; a snap ring A and a snap ring B are
mounted in the ring groove A and ring groove B of the transmission
shaft respectively; a convex ring is disposed on the side of the
snap ring A and the convex ring is sleeved on the transmission
shaft; the outer ring surface of the convex ring is mounted with a
thrust bearing; the three-stage sun gear is sleeved on the
transmission shaft and the three-stage sun gear is located between
the thrust bearing and the snap ring B; one side of the three-stage
sun gear is in contact with the thrust bearing, and the other side
is in contact with the snap ring B.
[0012] Preferably, one of the two arc blocks A has a notch A; and
one of the two arc blocks B has a notch B; the notch A is located
oppositely to the notch B; one end of the rectangular spring is
fixedly mounted in the notch A of the arc block A, and the other
end is fixedly mounted in the notch B of the arc block B. The
design of mounting at both ends of notch A, notch B and rectangular
spring is that, the two ends of the rectangular spring are
connected to the arc block A and the arc block B respectively when
the rectangular spring is compressed, to achieve better bearing
capacity; in addition, notch A and notch B can accommodate the ends
of the rectangular spring, which facilitates the fitting of the arc
block A and corresponding arc block B.
[0013] Preferably, two guide grooves are provided symmetrically
inside the chute B of the convex column B; two guide blocks are
disposed symmetrically on the outer wall at one end of the
transmission shaft in the chute B; the two guide blocks slide in
the two guide grooves respectively. The design of the guide blocks
and guide grooves makes the spring A always in a compressed state
and prevents one end of the transmission shaft from separating from
coupling B.
[0014] Preferably, the chute B of the convex column B is internal
regular hexagonal, the outer wall of the transmission shaft is
external regular hexagonal, and the outer wall of the transmission
shaft and the inner wall of the chute B are surface-to-surface
sliding. By this way, it facilitates the convex column B of
coupling B to drive the transmission shaft to rotate.
[0015] Preferably, two guide rails are mounted symmetrically in the
center of inner ring surface of the circular cavity in the disk B;
the two guide rails are in communication with the two chutes A
respectively; the two gear racks slide on the two guide rails
respectively. The design of the guide rail stabilizes the movement
of the gear rack and prevents the gear rack from shifting during
movement.
[0016] Preferably, a telescopic groove is provided at one end of
the gear rack; the sliding block is slidably mounted in the
telescopic groove; one end of the spring B located in the
telescopic groove is connected to the telescopic groove surface,
and the other end is connected to the sliding block.
[0017] Preferably, the outer wall of the rectangular spring is a
friction surface; one end of the tooth socket is a straight groove
face, and the other end is an arc groove face; the end of the
sliding block away from the spring B is a cambered surface, to
facilitate the sliding block to slide smoothly in the corresponding
tooth socket.
[0018] Preferably, the clutch is composed of a clutch handle, a
clutch sleeve and a clutch slider; the outer side of the housing is
rotatably mounted with a clutch handle, and the clutch sleeve
located in the housing is fixedly connected with the clutch handle;
two spiral structures are symmetrically disposed on the clutch
sleeve; the clutch slider is slidably mounted in the housing along
the axial direction of the transmission shaft, the two spiral
structures on the clutch sleeve mate with the clutch slider such
that the clutch slider moves axially; the axial movement of clutch
slider is controlled by rotating the clutch handle to drive the
clutch sleeve to rotate. In the present invention, refer to the
prior art for the specific mounting of the clutch handle, clutch
sleeve and clutch slider.
[0019] Compared to the conventional winch, the present invention
can achieve the following beneficial effects.
[0020] 1. The innovative improvement of the structure of the
engagement between the three-stage sun gear and the two-stage
planet carrier increases the distance between the adjacent internal
teeth of the two-stage planet carrier, which ensures that the
three-stage sun gear can be smoothly inserted into the two-stage
planet carrier even if the elasticity of spring A is reduced, such
that the engagement width between the three-stage sun gear and the
two-stage planet carrier can reach the normal requirements. With
the design of sliding gear ring and spring C, it can greatly reduce
the phenomenon of mis-engagement when the external teeth of the
three-stage sun gear enter the internal teeth spacing of the
two-stage planet carrier, protect the teeth integrity of the
three-stage sun gear and the two-stage planet carrier, and extend
the service life.
[0021] 2. By improving the structure, the brake unit herein can
achieve better braking effect than a transmission brake unit. Even
if the friction failure occurs after the rectangular spring is used
for a long time, the present invention can realize the complete
braking of coupling B and friction ring by sliding the gear rack
and sliding block into the tooth socket in the friction ring,
thereby the indirect braking between the transmission shaft and the
drum can be realized, ensuring that the winch still plays a role of
limit protection for the drum after power failure during the
working process.
BRIEF DESCRIPTION OF THE DRAWINGS
[0022] FIG. 1 is an overall and cross-sectional view of a
winch.
[0023] FIG. 2 is a partial enlarged view (I) of FIG. 1.
[0024] FIG. 3 is a partial enlarged view (II) of FIG. 1.
[0025] FIG. 4 is a view of a clutch part.
[0026] FIG. 5 is a cross-sectional view of clutch.
[0027] FIG. 6 is a cross-sectional view of an internal transmission
structure of winch.
[0028] FIG. 7 is a cross-sectional view showing the mating between
a gear rack and a gear wheel.
[0029] FIG. 8 is a partial enlarged front view of FIG. 7.
[0030] FIG. 9 is a cross-sectional view of a friction ring, a disk
B and a gear rack.
[0031] FIG. 10 is a structural view of a coupling A.
[0032] FIG. 11 is a structural view of a coupling B.
[0033] FIG. 12 is a cross-sectional view showing mating between a
three-stage sun gear and a two-stage planet carrier.
[0034] FIG. 13 is a partial enlarged view of FIG. 12.
[0035] FIG. 14 is the mounting cross-sectional view and mounting
front view of a sliding gear ring.
[0036] FIG. 15 is a partial view of a transmission shaft and a
cross-sectional view of a three-stage sun gear.
[0037] FIG. 16 is a view showing engagement of a three-stage sun
gear and a two-stage planet carrier and a partial enlarged view
thereof.
[0038] FIG. 17 is a mounting view of a rectangular spring.
[0039] Notes: 1, housing; 2, motor module; 3, drum; 4, clutch; 5,
transmission shaft; 6, one-stage deceleration assembly; 7,
two-stage deceleration assembly; 8, three-stage deceleration
assembly; 9, brake unit; 10, motor; 12, rotary shaft; 13, gear
wheel; 14, coupling A; 15, bracket; 16, friction ring; 17,
rectangular spring; 18, coupling B; 19, spring A; 20, two-stage
planet carrier; 21, three-stage sun gear; 22, sliding gear ring;
23, snap ring A; 24, snap ring B; 25, clutch handle; 26, clutch
sleeve; 27, clutch slider; 28, gear rack; 29, tooth socket; 30,
sliding block; 31, spring B; 32, guide rail; 33, chute A; 34,
telescopic groove; 35, disk A; 36, convex column A; 37, arc block
A; 38, notch A; 39, disk B; 40, convex column B; 41, arc block B;
42, notch B; 43, circular cavity; 44, guide groove; 45, guide
block; 46, two-stage planetary gear; 47, three-stage planetary
gear; 48, thrust bearing; 49, inner ring; 50, spring C; 51,
electronic control module; 52, ring groove A; 53, ring groove B;
54, convex ring; 55, convex wear ring; 56, chute B.
DETAILED DESCRIPTION
[0040] The present invention will be described with reference to
the accompanying drawings; however, it should be understood that
the structural proportions in the accompanying drawings are only
exemplary, and are not intended to limit the scope of the present
disclosure.
[0041] As shown in FIG. 1, a winch, comprising: a housing 1, an
electric control module 51 mounted in the upper side of the housing
1, a motor module 2 mounted in the left end side of the housing and
a deceleration module and a clutch 4 mounted in the right end side
of the housing 1, and a drum 3 mounted in the middle of the lower
side of the housing 1, the motor 10 in the motor module 2 drives
the transmission shaft 5 in the drum 3 to rotate through a brake
unit 9, the transmission shaft 5 drives the drum 3 to rotate
through the deceleration module, and the clutch 4 controls the
axial movement of the transmission shaft 5; as shown in FIG. 3, the
deceleration module is composed of a one-stage deceleration
assembly 6, a two-stage deceleration assembly 7 and a three-stage
deceleration assembly 8; as shown in FIGS. 12, 13 and 14, a sliding
gear ring 22 is slidably mounted in a two-stage planet carrier 20
in the two-stage deceleration assembly 7, and the external teeth of
the sliding gear ring 22 are always in engagement with internal
teeth in the two-stage planet carrier 20; One end of a spring C 50
located in the two-stage planet carrier 20 is connected to the
sliding gear ring 22, and the other end is connected to the inner
ring 49 of the center hole of the two-stage planet carrier 20; a
three-stage sun gear 21 in the three-stage deceleration assembly 8
mates with a convex wear ring 55 on the side of the sliding gear
ring 22; the three-stage sun gear 21 always follows the
transmission shaft 5 for synchronous axial movement; as shown in
FIG. 16, the size of any one of external teeth on the three-stage
sun gear 21 is smaller than the spacing between any two adjacent
internal teeth of the two-stage planet carrier 20.
[0042] The brake unit 9 comprises a coupling A 14, a coupling B 18,
a rectangular spring 17, a gear wheel 13, and a gear rack 28, as
shown in FIG. 10, wherein a convex column A 36 is disposed on the
side of disk A 35 of the coupling A 14, and two arc blocks A 37 are
symmetrically disposed on the outer cylindrical surface of the
convex column A 36; as shown in FIG. 11, a convex column B 40 is
disposed on one side of disk B 39 of the coupling B 18, and two arc
blocks B 41 are symmetrically disposed on the other side; one end
of the transmission shaft 5 is slidably mounted in the chute B 56
of the convex column B 40; a spring A 19 is mounted between the
groove surface of the chute B 56 and the corresponding end surface
of the transmission shaft 5 is always in a compressed state; as
shown in FIGS. 9 and 11, a circular cavity 43 is disposed in the
disk B 39, and two chutes A 33 are symmetrically provided in the
center on the inner ring surface of the circular cavity 43; as
shown in FIG. 17, two arc blocks B 41 are sleeved on the convex
column A 36, and the two arc blocks B 41 mate with two arc blocks A
37 respectively; as shown in FIGS. 2 and 8, one end of a rotary
shaft 12 is fixedly connected to the end of the convex column A 36
away from the disk A 35, and the other end penetrates into the
circular cavity 43 of the disk B 39 and is fixedly equipped with a
gear wheel 13; two gear racks 28 engaged with the gear wheel 13
slide on the two chutes A 33, respectively; the ends of two gear
racks 28 away from each other are slidably mounted with a sliding
block 30 through a spring B 31; as shown in FIG. 17, one end of a
rectangular spring 17 sleeved on the arc block A 37 and the arc
block B 41 is connected with an arc block A 37, and the other end
is connected with an arc block B 41.
[0043] As shown in FIGS. 6 and 7, a bracket 15 is disposed in the
housing 1 and a friction ring 16 is disposed at the center of the
side of the bracket 15, the friction ring 16 is located in the drum
3; the coupling A 14 and the coupling B 18 are both located in the
friction ring 16; as shown in FIGS. 8 and 9, two tooth sockets 29
are provided symmetrically in the center of the inner ring surface
at one end of the friction ring 16; two sliding blocks 30 on the
two gear racks 28 mate with the two tooth sockets 29 respectively;
as shown in FIGS. 2 and 6, the rectangular spring 17 mates with the
friction ring 16.
[0044] As shown in FIGS. 13 and 15, the transmission shaft 5 is
provided with a ring groove A 52 and a ring groove B 53; a snap
ring A 23 and a snap ring B 24 are mounted in the ring groove A 52
and ring groove B 53 of the transmission shaft 5 respectively; a
convex ring 54 is disposed on the side of the snap ring A 23 and
the convex ring 54 is sleeved on the transmission shaft 5; the
outer ring surface of the convex ring 54 is mounted with a thrust
bearing 48; the three-stage sun gear 21 is sleeved on the
transmission shaft 5 and the three-stage sun gear 21 is located
between the thrust bearing 48 and the snap ring B 24; one side of
the three-stage sun gear 21 is in contact with the thrust bearing
48, and the other side is in contact with the snap ring B 24.
[0045] As shown in FIGS. 10, 11 and 17, one of the two arc blocks A
37 has a notch A 38; and one of the two arc blocks B 41 has a notch
B 42; the notch A 38 is located oppositely to the notch B 42; one
end of the rectangular spring 17 is fixedly mounted in the notch A
38 of the arc block A 37, and the other end is fixedly mounted in
the notch B 42 of the arc block B 41.
[0046] As shown in FIG. 11, two guide grooves 44 are provided
symmetrically inside the chute B 56 of the convex column B 40; two
guide blocks 45 are disposed symmetrically on the outer wall at one
end of the transmission shaft 5 in the chute B 56; the two guide
blocks 45 slide in the two guide grooves 44 respectively.
[0047] The chute B 56 of the convex column B 40 is internal regular
hexagonal, the outer wall of the transmission shaft 5 is external
regular hexagonal, and the outer wall of the transmission shaft 5
and the inner wall of the chute B 56 are surface-to-surface
sliding.
[0048] As shown in FIGS. 8 and 9, two guide rails 32 are mounted
symmetrically in the center of inner ring surface of the circular
cavity 43 in the disk B 39; the two guide rails 32 are in
communication with the two chutes A 33 respectively; the two gear
racks 28 slide on the two guide rails 32 respectively.
[0049] As shown in FIG. 9, a telescopic groove 34 is provided at
one end of the gear rack 28; the sliding block 30 is slidably
mounted in the telescopic groove 34; one end of the spring B 31
located in the telescopic groove 34 is connected to the telescopic
groove 34 surface, and the other end is connected to the sliding
block 30.
[0050] The outer wall of the rectangular spring 17 is a friction
surface; one end of the tooth socket 29 is a straight groove face,
and the other end is an arc groove face; the end of the sliding
block 30 away from the spring B 31 is a cambered surface.
[0051] As shown in FIGS. 4 and 5, the clutch 4 is composed of a
clutch handle 25, a clutch sleeve 26 and a clutch slider 27; the
outer side of the housing 1 is rotatably mounted with a clutch
handle 25, and the clutch sleeve 26 located in the housing 1 is
fixedly connected with the clutch handle 25; two spiral structures
are symmetrically disposed on the clutch sleeve 26; the clutch
slider 27 is slidably mounted in the housing 1 along the axial
direction of the transmission shaft 5, the two spiral structures on
the clutch sleeve 26 mate with the clutch slider 27 such that the
clutch slider 27 moves axially; the axial movement of clutch slider
27 is controlled by rotating the clutch handle 25 to drive the
clutch sleeve 26 to rotate.
[0052] The sliding of the sliding block 30 of the present invention
in the telescopic groove 34 of the gear rack 28 can be mounted in a
mating manner between the guide block 45 and the guide groove 44,
to ensure that the gear rack 28 can pull the sliding block 30 to
follow the gear rack 28 to synchronize movement through the guide
block 45 when moving in a direction away from the corresponding
tooth socket 29.
[0053] In the present invention, the thrust bearing 48 is mounted
on the convex ring 54 of the snap ring A23. It can achieve the
following function:
[0054] The function of the snap ring A23 is to push the three-stage
sun gear 21 through the thrust bearing 48. During the three-stage
sun gear 21 is pushed, the three-stage sun gear 21 can be smoothly
rotated under the action of the thrust bearing 48, so that the
three-stage sun gear 21 will not cause frictional obstacles with
the snap ring A23.
[0055] In the present invention, a one-stage deceleration assembly
6 is composed of a one-stage sun gear, a one-stage planetary gear,
a one-stage planet carrier and a one-stage gear ring; a two-stage
deceleration assembly 7 is composed of a two-stage sun gear, a
two-stage planetary gear 46, a two-stage planet carrier 20 and a
two-stage gear ring; a three-stage deceleration assembly 8 is
composed of a three-stage sun gear 21, a three-stage planetary gear
47, a three-stage planet carrier and a three-stage gear ring; the
transmission shaft 5 drives the two-stage deceleration assembly 7
to move through the one-stage deceleration assembly 6, the
two-stage planet carrier 20 in the two-stage deceleration assembly
7 is transmissibly mated with the three-stage sun gear 21 in the
three-stage deceleration assembly 8, and the three-stage
deceleration assembly 8 is transmissibly connected with the drum
3.
[0056] In the present invention, the snap ring B 24 and the
three-stage sun gear 21 are in sliding friction fit.
[0057] In the present invention, the spacing between internal teeth
of the two-stage planet carrier 20 is reasonably designed while
ensuring the strength of the internal teeth.
[0058] In the present invention, the rectangular spring 17 has the
following roles: firstly, the rectangular spring 17 and the
friction ring 16 can produce a friction braking effect; secondly,
the deformation of the rectangular spring 17 can effectively buffer
the impact between the arc block A 37 and the arc block B 41,
playing a protective role.
[0059] The specific working process of the present invention is
described as follows. In the initial state when the winch is not in
use, the three-stage sun gear 21 engages with the two-stage planet
carrier 20, the spring C50 is in a compressed state, and the convex
wear ring 55 on the sliding gear ring 22 is in frictional contact
with the side of the three-stage sun gear 21; the spring A 19 is in
a compressed state, and the guide block 45 is located at one end of
the guide groove 44 away from the disk B39; the outer diameter of
the rectangular spring 17 reaches the maximum and the outer
diameter of the rectangular spring 17 is in friction braking with
the inner ring surface of the friction ring 16; the side of the arc
block A 37 fits the side of the arc block B 41. In this state, the
drum 3 on the winch cannot release the twisted rope. The gear rack
28 is located in the corresponding guide rail 32 and chute A 33;
the sliding block 30 on the gear rack 28 is located in the
corresponding tooth socket 29 and fits the straight groove face of
the corresponding tooth socket 29; or the sliding block 30 on the
gear rack 28 is in contact with the inner ring surface of the
friction ring 16, the sliding block 30 does not enter the
corresponding tooth socket 29, and the spring B 31 is in a
compressed state. In the following description, the sliding block
30 located in the corresponding tooth socket 29 is used as a
reference example.
[0060] When the winch needs to release the twisted rope, the clutch
handle 25 is manually rotated, the clutch handle 25 pushes the
clutch slider 27 to move towards the drum 3 through the clutch
sleeve 26, the clutch slider 27 pushes the transmission shaft 5 to
move towards the motor 10. The transmission shaft 5 pushes the
three-stage sun gear 21 to move synchronously through the snap ring
B24 and the snap ring A 23 in a clamping manner, and the
three-stage sun gear 21 is disengaged from the two-stage planet
carrier 20. When the transmission shaft 5 is pushed to the limit
position, the force of the clutch handle 25 is removed, and the
position of the clutch slider 27 remains unchanged. During the
synchronous movement of the transmission shaft 5 and the
three-stage sun gear 21, under the reset action of spring C 50, the
sliding gear ring 22 moves to reset towards the three-stage sun
gear 21, and the sliding gear ring 22 will never be detached from
the two-stage planet carrier 20 during the reset process. Under the
pushing of the transmission shaft 5, the spring A19 continues to be
compressed, and the guide block 45 follows the transmission shaft 5
to move in the guide groove 44. Since the three-stage sun gear 21
is not engaged with the two-stage planet carrier 20 any longer, the
power transmission between the transmission shaft 5 and drum 3 will
no longer exist, and the transmission shaft 5 will still restrict
the rotation of the one-stage deceleration assembly 6 and the
two-stage deceleration assembly 7. The rotation restriction of the
three-stage deceleration assembly 8 and the two-stage deceleration
assembly 7 is removed, thereby the rotation of the drum 3 is not
indirectly restricted by the transmission shaft 5 any longer; by
this way, the twisted rope on the winch can be released.
[0061] When it is necessary to re-wind the released twist rope on
drum 3, the clutch handle 25 is reversely rotated to make the
clutch sleeve 26 to rotate reversely. During the process, under the
reset action of spring A 19, the transmission shaft 5 pushes the
clutch slider 27 to move to reset along the guided cambered surface
rail. The transmission shaft 5 pushes the three-stage sun gear 21
to move synchronously through snap ring B 24 and snap ring A 23 in
a clamping manner; when the external teeth of three-stage sun gear
21 are exactly opposite to the spacing of internal teeth of the
two-stage planet carrier 20, the external teeth of the three-stage
sun gear 21 can quickly and smoothly insert into the spacing of the
internal teeth of the two-stage planet carrier 20 to achieve the
engagement between them. The three-stage sun gear 21 pushes the
sliding gear ring 22 to move, and the spring C 50 is compressed
again; when the transmission shaft 5 drives the guide block 45 to
move to the end of the guide groove 44 away from the disk B 39, the
transmission shaft 5 will not continue to move any longer, at this
time, the width of engagement between the three-stage sun gear 21
and the two-stage planet carrier 20 reaches the normal
requirements. When the twisted rope is manually pulled in this
state, since the three-stage sun gear 21 is engaged with the
two-stage planet carrier 20, the indirect braking relationship
occurs again between the drum 3 and the transmission shaft 5. When
the drum 3 is not rotated, it represents the three-stage sun gear
21 has been engaged with the two-stage planet carrier 20. When the
external teeth of the three-stage sun gear 21 are not opposite to
the spacing of the internal teeth of the two-stage planet carrier
20, the twisted rope is pulled to make the drum 3 rotate at a
certain angle, drum 3 drives the three-stage deceleration assembly
8 to make the three-stage sun gear 21 rotate at a certain angle,
during the rotation, the external teeth of the three-stage sun gear
21 will be exactly opposite to the spacing of the internal teeth of
the two-stage planet carrier 20. In such case, the process of
inserting the three-stage sun gear 21 into the two-stage planet
carrier 20 and generating the engagement is carried out
repeatedly.
[0062] When a user forgets to pull the twisted rope and the
external teeth of the three-stage sun gear 21 are not opposite to
the spacing of the internal teeth of the two-stage planet carrier
20, the side of the three-stage sun gear 21 fits the side of the
two-stage planet carrier 20, and the user starts the motor 10. The
motor 10 axis drives the coupling A 14, the rotary shaft 12 and the
gear wheel 13 to rotate; the gear wheel 13 drives the two gear
racks 28 to move, and the two gear racks 28 move in opposite
directions. The gear rack 28 pulls the sliding block 30 to follow
the gear rack 28 to move synchronously by mounting the spring B 31
or the traditional guide groove 44 and guide block 45, the sliding
block 30 separates from the corresponding tooth socket 29, the
friction ring 16 and disk B 39 are no longer connected as a whole,
and the braking of the coupling B 18 and friction ring 16 is
released; as shown in FIG. 17, the arc block A 37 on coupling A 14
moves towards another arc block B 41 until it has a toggle fit with
the arc block B 41. During the process, the rectangular spring 17
is compressed, and the outer diameter of the rectangular spring 17
becomes smaller, such that the rectangular spring 17 does not
generate friction braking with the friction ring 16 any longer.
When the arc block A 37 toggles the arc block B 41 to rotate, the
coupling A 14 and the coupling B 18 rotate synchronously, and the
gear wheel 13 and the gear rack 28 will also rotate synchronously.
The gear wheel 13 will not drive the gear rack 28 to continue to
move along the guide rail 32; in this state, braking will not occur
between the rectangular spring 17 or the coupling B 18 and the
friction ring 16, and the coupling A 14 drives the transmission
shaft 5 to rotate via the coupling B18.
[0063] The transmission shaft 5 drives the two-stage deceleration
assembly 7 to rotate through the one-stage deceleration assembly 6,
and rotate the two-stage planet carrier 20 in the two-stage
deceleration assembly 7; when the external teeth of the three-stage
sun gear 21 are opposite to the spacing of the internal teeth of
the two-stage planet carrier 20, under the reset action of spring A
19, the transmission shaft 5 pushes the three-stage sun gear 21 to
insert into the spacing of the internal teeth of the two-stage
planet carrier 20 through the snap ring B 24 and snap ring A 23 in
a clamping manner. During the process, the side of the three-stage
sun gear 21 and the convex wear ring 55 on the sliding gear ring 22
are always in frictional contact. Under the action of friction, the
sliding gear ring 22 can make the three-stage sun gear 21 to
rotate, such that the three-stage sun gear 21 can quickly change
from the original non-rotating state to the rotated state, and the
speed relative to the two-stage planet carrier becomes small, to
reduce the impact, so that the three-stage sun gear 21 can be
smoothly inserted into the two-stage planet carrier 20.
[0064] As shown in FIG. 16, in the present invention, the spacing
between internal teeth of the two-stage planet carrier 20 should be
designed to be greater than the size of external teeth of the
three-stage sun gear 21 for the following reasons: firstly, it is
to allow the external teeth of the three-stage sun gear 21 to have
sufficient time to insert into the spacing of the internal teeth of
the two-stage planet carrier 20 smoothly; secondly, in the process
of inserting the three-stage sun gear 21 into the two-stage planet
carrier 20, in the rotation driving direction of the two-stage
planet carrier 20, the three-stage sun gear 21 obtains the speed,
and its speed relative to the two-stage planet carrier 20 is
reduced, so the toggle tooth surface in the rotation drive
direction of internal teeth of the two-stage planet carrier 20
needs some time to toggle the toggled teeth surface in the external
teeth rotation drive direction of the three-stage sun gear 21,
during the period, the non-toggle teeth surface in the external
teeth rotation drive direction of the three-stage sun gear 21 has a
very small friction with the non-toggle teeth surface in the
internal teeth rotation drive direction of the two-stage planet
carrier 20, which is very convenient for the three-stage sun gear
21 to insert into the two-stage planet carrier 20 rapidly and
smoothly.
[0065] When the transmission shaft 5 drives the guide block 45 to
move to the end of the guide groove 44 away from the disk B39, the
transmission shaft 5 does not continue to move. At this time, the
width of engagement between the three-stage sun gear 21 and the
two-stage planet carrier 20 meets the normal requirements, and the
sliding gear ring 22 restores to the initial position. As the
two-stage planet carrier 20 continues to rotate and drive, the
two-stage planet carrier 20 drives the three-stage sun gear 21 to
rotate synchronously; the two-stage deceleration assembly 7 is
transmissibly connected with the three-stage deceleration assembly
8, and the drum 3 can rotate and wind the twisted rope.
[0066] When the winch is stopped according to actual needs, the
motor 10 is powered off. Under the reset force of the rectangular
spring 17, the coupling A 14 will be rotated in the opposite
direction relative to the coupling B 18, and the arc block A 37 on
the coupling A 14 will move towards the arc block B 41 on the
coupling B 18 in the initial state until the side of the arc block
A 37 fits the side of the arc block B 41 to restore to the original
state. The outer diameter of the rectangular spring 17 is restored
to the maximum in the initial state, and a friction braking occurs
between the outer diameter of the rectangular spring 17 and the
inner ring surface of the friction ring 16. During the reverse
rotation of the coupling A 14, the coupling A 14 makes gear wheel
13 to rotate reversely, and the gear wheel 13 drives the two gear
racks 28 to move toward the initial position, and the two gear
racks 28 move oppositely. The sliding block 30 on the two gear
racks 28 are slidably mated with the inner ring surface of the
friction ring 16, and the spring B 31 is in a compressed state; the
sliding block 30 slides along the inner ring surface of the
friction ring 16 into the corresponding tooth socket 29. After the
gear rack 28 connects the friction ring 16 with the coupling B 18
as a whole, under the obstacles of the gear rack 28, sliding block
30 and tooth socket 29, braking will occur on the friction ring 16
and coupling B18 in the direction in which the drum 3 releases the
twisted rope.
[0067] Although the present invention is described in conjunction
with the foregoing embodiments, it is not limited to the foregoing
embodiments, but limited by the appended claims. A person of
ordinary skill in the art can easily perform modifications and
changes to them without departing from the essential concept and
scope of the present invention.
* * * * *